Reproducing machine



July 3, 1951 D. R. TRINKLE 2,559,097

REPRODUCING MACHINE Filed March 22, 1950 8 Sheets-Shawl 1 INVENTOR.

lDALLAS R. TRINKLE ATTORNEYS July 3, 1951 D. R. TRINKLE 2,559,097

REPRODUCING MACHINE Filed March 22, 1950 8 Sheets-Sheet 2 INVENTOR.

DALLAS R. TRINKLEv ATTORNEYS July 3, 1951 D. R. TRINKLE 2,559,097

REPRODUCING MACHINE Filed March 22, 1950 8 Sheets-Sheet 5 oo r N Ch L v'0 f\ Ln N7 N l0\- r? V q. m I 1 I I FIG. 3

INVENTOR. DALLAS R TRINKLE ATTORNEYS July 3, 1951 D. R. TRINKLE2,559,097

REPRODUCING MACHINE Filed March 22, 1950 8 Sheets-Sheet 4 D S CINI/MIUR.

DALLAS R. TRINKLE BY f @www Y Q/cggi':

ATTORNEYS- July 3, 1951 D. R.y TRINKLE 2,559,097

REPRODUCING MACHINE v Filed Marsh 22, 195o s sheets-sheet 5 INVENTOR.

DALLAS RTRINKLE ATTORNEYSv FIG.8

July 3, 1951 D. R.,TR|NKLE Y 2,559,097

REPRODCING MACHINE Filed March 22, 195o 8 sheets-sheet 7 E 8 INVENTOR.

. DALLAS R. TRNKLE BY i ATTORNEYS July 3, 1951 D. R. TRINKLE 2,559,097

` v REPRODUCING MACHINE Filed llarch 22, l1950 8 Sheets-Sheet 8 INVENroADALLA-s R. TRINKLE v Y BY Y ATTORNEYS `Patented July 3, 1951 UNITEDsTATEs- PATENT oFncE Dallas R. Trinkle, Cincinnati, Ohio, The CincinnatiVMilling Machine.

nati, Ohio, a corporation of Ohio Application March 22, 1950, Serial No.151,194 16- Claims. (Cl. 90-13.5)

'I'his invention relates to improvements in machines for production ofwork pieces in accordance with a layout or pattern and has particularreference to machines for performing profiling or contouring operations.

One of the objects of the present invention is the provision of amachine of this character which may be employed for direct reproductionof the pattern or layout or for proportional variation of one or both ofits dimensions. l

A further object of the invention is to provide a readily adjustablesize. determining mechanism for accurately controlling the relationshipbetween the relative movements of the pattern and follower with respectto the directionally controlled relative movements between the workpiece and forming tool.

Another object is to provide a reproducing machine embodying improvedaccurate control at selected proportional rates of the power effectedrelative movements of Aa cutterand work piece in prescribed proportionalrelationship to concurrently effected relative movements of a layout orpattern and a pattern following member.

A more specific object of the present invention is the provision of amachine embodying individually controllable ratio determining means foreach direction of relative movement of a pattern and afollowerestablishing the basis design of the shape to be produced. which willmodify the nature and extent of the relative movements of cutter andwork asA respects those of the pattern and follower.

A further object of the invention is the provision of an adjustableratio determining mechanism which may be employed with either directmechanical, hydraulic or other power amplifying mechanism fordetermination of the final size and shape of work piece produced.

Other objects and advantages of the present invention should be readilyapparent by reference to the following specication, consideredinconjunction with the accompanying drawings forming a part thereof, andit is to be understood that any modifications may be made in the exactstructural details there shown and described, within the scope of theappended claims, without departing from or exceeding the spirit of theinvention.

Figure 1 is a front elevation of one embodiment of the invention.

Figure 2 is an end-elevation thereof with parts broken away.

YFigure 3 is a horizontal sectional view taken Vsubstantially on theline 3-3 of Figure 1.

2 Figure 4 is a vertical sectional view as'on th line H of Figure 3.

Figure 5 is a fragmentary sectional-view of the servo-valve mechanisminelevation.

Figure 6 is a fragmentary plan view of the I servo-valve mechanism withparts broken away. Figure 7' is a fragmentary horizontal sectional vView taken on the line 1-1 of Figure 1.

Figure 8 is a vertical section as on the line 8-8 of Figure 7.

Figure 9 is an expanded sectional view taken on line 9-9 of Figure 8.

Figure 10 is a fragmentary vertical'section onl the linen-l0 of Figure1.

Figure 11 is a fragmentary vertical sectional view on the line Il ll ofFigure 1.

Figure 12 is a diagrammatical view of the hydraulic actuating circuitsand related control parts -of the machine.

Figure 13 is a dia'grammatical view of the electrical circuits forautomatic trol.

In the drawings the numeral 20 indicates the bed ofthe machine providedwith longitudinal pattern tracing conways 2i on which is mounted forlongitudinal n movement the table 22 carrying the work piece or workpieces 23. As illustrated in Figure 1, the bed is also provided at itsright hand portion with the additional ways 24 for the layout or patternsupporting table 25 movable transversely as respects the bed orin a pathat right angles to the direction table 22.

Rising from the bed 20 is the column portion 26 having on its upper facethe ways 21 for the transversely moving ram 28. The ram carries thecutter spindles 29 whose vertical position may be determined by the handwheels 30 and which in use are provided with cutters as indicated at 3|.

Laterally extending from the column portion 26 is a horizontal frame 32having ways 33 on which is slidably'mounted for longitudinal adjustmentthe tracer unit34 from which depends the tracer head 35 carrying tracerpoints 36 adapted to follow the layout'or pattern 31- supported by thetable 25. .v

As indicated in Figures 1, 10, and 12, a cylinder 38 is secured to thebed 20 and contains the reciprocating piston 39 coupled by piston rod 40to bracket 4| to eifect the forward and rearward movement of the table25.v Dependingl from said table is a cylindrical stud I2 on which isrotatably mounted the hub 43 of Worm Agear segment 44 as also shown inFigures 4 and 7. The flange f the movementof the carrying table 22 willbe the same as that of portion 46 is mounted to the hub 48 by suitablescrew connections to provide end support for hub 43 in the'bracket 46.The worm gear segment 44 meshes with the worm 41 that is secured toshaft 48 provided with the adjusting dial 49. The shaft 48 is journaledin a bracket 50 that is secured to the table 25 as shown in Figures 1,3, and 4, and moves in a transverse direction with the table. In the bed20 is a horizontal slot 5| that provides clearance for shaft 48 as thetable is moved transversely on its ways. A downwardly extending flangeor sine bar 52 on the worm gear segment 44 is provided for cooperationwith the servo-valve unit generally indicated by 53 and shown in detailin Figures and 6. This unit has a shoe 54 and spring operated plungers55 cooperating with springs 56 as indicated in Figures 5 and 6 to pressthe surface 51 of the downwardly extending flange 52 against the surface58 of shoe 54 to provide a slidable fit between the members and preventlost motion or any independent relative movement m a plane perpendicularto the direction of travel. Connected to the shoe 54 is the plunger 59which is provided with a spool 60 that cooperates with the ports in thecasing 6|. The servo-valve unit 53 operates the hydraulic actuatingcylinder 62 in a manner hereinafter disclosed in detail. The cylinder 62has a piston 63 which operates the piston rod 64 connected to the workcarrying table 22 by the bracket 65.

The casing of the servo-valve 53 is connected to the stud 66 which ispivoted to the arm 61 that moves longitudinally with the Work table 22.

For set-up purposes, the arm 61 is adjustably connected to the table 22by a construction shown in detail in Figures 1, 2, and 7. Thisadjustment is determined by the rotation of the dial 68 on the leadscrew 69 that is threaded into a section of the arm 61. The lead screw69 is journaled for rotation in the work table bracket 65 and is heldfrom independent axial movement by the collar 18 and the dial 68.

Transverse horizontal movement of the layout carrying table 25 will movethe downwardly extending flange4 52 in a transverse path and due to itsangular position as determined by the dial 49, a predetermined relativemovement of the work carrying table 22 will be effected in alongitudinal direction or at right angles to the directionof movement ofthe layout carrying table 25. Rotation of dial 49 will adjust the sinebar 52 to any angularqposition, ranging from one that is parallel to thedirection of movement of table 25. toa position that is 90 degreestherefrom. If the angular position of the sine bar 62 is at 45 degreesto the direction of travel of the table 25 then the rate or amount ofmovement of the work the layout or template carrying table 25. l

The tracer unit 34, as has been previously described, is mounted on theways 33 for longitudinal movement in a plane substantially at rightangles to that of the table` 25. As shown in Figures 1, 3, 4, and 11,the arm 1| is connected with the ,tracer unit 34 for longitudinalmovement therewith and has the shoe 12 in the opposite end thereof thatmoves between the bars 13 that are mounted on the vertical column 26.Rotatably connected to .the shoe 12 is the stud 14 that is secured tothe worm gear segment 15 which cooperates with the worm 16 on thesplined shaft 11. The angular position of the shaft 11 may be adjustedby a, dial 18 which is similar to the dial 49 previously described. Thesegment 15 has an upwardly extending flange or sine bar surface 19 thatcooperates with the shoe 80 of a servovalve unit which is identical inconstruction and function to that shown in Figures 5 and 6. The casing8| of the servo-valve is connected to the cylindrical stud 82 which ismounted for rotation in the slidably adjustable shoe 83. that is carriedby the 'ram 28. The feed screw 84, the dial and square external portionof which is-shown in Figure '1. is threaded into the rectangular shoe 83in a manner similar to that described for lead screw 69 and the arm 61.Rotation of screw 84 by a suitable crank will enable the ram and itsassociated cutters 3| to be moved independent of the tracer unit 34 forset-up purposes.

Longitudinal movement of the tracer unit 34 is accomplished by thehydraulic cylinder 85 having a piston 86 connected to the piston rod 81that is secured to the column 26 by bracket 88. The servo-valve casing8| is connected by 20 conduits, hereinafter described,.to the hydrauliction of movement of the tracer unit 34, no resultant movement of the ram28 will be accomplished by movement of the tracer unit, but when thesine bar 19 is turned out of parallel alignment with the transversetravel of the tracer unit the hydraulicsystem, hereafter described, willproduce relative movement of the ram 28.

As pointed out heretofore, if the adjustment oi the sine bar is suchthat it will bear a 45 degree angular relationship with the movement ofthe tracer unit 34, then the movement of the ram will be equal to thatof the tracer unit.

The micrometer dial means for effecting accurate minute adjustments ofthe sine bar segments 44 and 15 is illustrated in detail in Figures 8and 9. 'I'he sine bar segments 15 and 44 are provided with one tooth onperiphery per degree of rotation and the worm gears 41 and 16 are singlethread so that one revolution of the shafts 48 or 11 will result in onedegree of angular disy placement of their sine bar segments.'I'herefore, the dial member 95 which is securely connected to theshaft, such as `by dog point set screw 96, is calibrated to read insixtieths of a degree or in minutes. The conventional vernier calibratedzero marker, such as 91, is provided for reading in divisions of aminute for rotational movement of the dial member 95. In order toindicate the number of revolutions of a dial member 95 that have beentaken from a position wherein the sine bar segments 44 and 15 are in apath parallel to the transverse and longitudinal movement of theirrespective driving means,

a graduated member 98 is provided which is num-l bered as at 99 to readin degrees. 'I'hese numbers are visible through the window to indicatethe amount of adjustment in degrees which has been imparted to the sinebar segments. For practical purposes, the gear reduction isapproximately 100 to 1 between the dial member 95 and the calibratedmember 98 so that any position of the sine bar segments 44 and 15 fromzero to degrees relative to the movement of their respective actuatingunits will be indicated through the window |08.

This gear reduction is accomplished by a pinion |0l| cut on the shafts48 and 11, meshing with a A spur gear lo: when is integral with thepinion |03. The pinion |03 meshes with a second spur gear |04 which hasan integral pinion |05 that meshes with the internal gear |06 formed inthe graduated member 98. The member 90 has its central portion bearingon a reduced cylindrical section of the shafts 48 and 11 and is axiallysupported between the bracket 60 and the dial member 95. The straightcylindrical sections |01 and |08 are extensions of the pinions |03 and|05 respectively and are journaled in the sleeves |09 and that arepressed into the bracket 50. Figure 8 shows diagrammatically the gearsin the actual meshed relationship but for the sake of illustration asection is shown in Figure.9 in expanded relation as indicated by theline 9-9 of Figure 8.

Figure 13 shows diagrammatically the electrical circuit for operation ofthe motor which rotates the tracer control cam |2| and the relatedvalves that will be hereinafter described. Connected to the shaft |22and rotated therewith are two tracer fingers |23 and |24 that areelectrically insulated from the frame of the machine and have theirrespective leads and |26 connected to the switch terminals |21 and |28.In this instance, the layout 31 is a conducting material and grounded tothe frame of the machine as at |29. The pattern line is of insulatingmaterial and is applied by conventional drafting 'equipment to asufficient thickness to provide'a controlling path for the tracerfingers and the tracer control unit as they are brought into contactwith the line. 'I'his is generally accomplished by causing the motor |20to rotate the shaft |22 and its associate cam |2| in a clockwisedirection whenever the tracer nger |23 contacts the line |30. As will bepointed out later, the change in angular position of the control cam |2|will produce a change ^in rate and feed of hydraulic fluid to the tracerhead hydraulic cylinder 85 or the layout table hydraulic cylinder 38 toproduce a change in the resultant movement between the tracer fingersand the prole layout.

Likewise, when the tracer finger |24 contacts the insulating prolelayout |30, the opposite electrical circuit of the motor |20 will beenabled and the rotation of shaft |22, the control cam |2|. and themounting for the tracing fingers |23 and |24 will be rotated in acounterclockwise directionso asvto move the tracer finger |24 out ofengagement with the `line |30 and into electrical contact with thelayout material 31.

t should also be pointed out that the intersection of the center linesindicated by |3| in Figure l2 indicates the axis of rotation of theshaft |22 and the control cam |2|. The tracer points are eccentricallyadvanced with respect to this axis of rotation in the direction ofrelative movement .between tracer and layout. As a result; contact ofone point or the other with the profile line will energize the motor |20to swing the contacting tracer point out of engagement with the line andeffect the required` change in direction of relative movement betweentracer axis 'and profile layout.

The motor |20 is of reversible, series wound, split-held, direct currenttype wherein the eld |32 will energize the motor for rotation of shaft|22 in. a clockwise direction and field |33 will produce the oppositeresult. A conventional type magnetic clutch is provided with thewinding|34 for engaging the armature of the motor |20 with the drive pinion |35which through connected gears produces rotation of the worm |36 and the.

worm gear that is connected to the shaft |22. Connected to the motorfield |32 is a lead 31 and to the field |33 is lead |30.

The clutch coil |34 is connected through the lead |39 to ground. Themotor eld |32 is ener- Sized by a pair of grid controlled rectifyingtubes |40 and, correspondingly, the motor field |33 is energized by asimilar pair of tubes |4|. When the tracer fingers are on opposite sidesof the line and both in electrical contact with the pattern layoutmaterial 31, the motor is inactive because the tubes |40 and |4| arebiased in nontransmitvting condition.

The positive side' of the battery |42 or suitable direct current supplyis connected through lead |43 through the switch |44 to the terminal |21and lead |25 to the tracer finger |23. The negative side is connected bylead |45 to the grid of the tubes 40. A high resistance bleeder |46 isprovided between the grids and ground |41. Tracer finger |23, being incontact with the grounded layout material 31 completes a bias circuit sothat the tubes l|40 do not conduct. As soon as the transverse movementof the table 25 or the longitudinal movement of tracer head 34 causesthe tracer finger |23 to engage the line |30, the positive batterycircuit to the ground will be broken and the bias will beremoved fromthe tubes |40 permitting them to fire. Resultant action will produceclockwise rotation of shaft |22 which will cause the tracer fingers toswing in clockwise rotation, bringing finger |23 out of contact with theinsulating line |30 and into contact with the grounded layout material31. This action will bias the tubes |40 to stop motor rotation, and ifthis angular adjust-ment of the control cam |2| produces suiiicientchange in the relative direction of movement between the tracer head andthe layout so that it will move parallel to the profile line, thetracing action will continue without motor rotation until either tracerfinger contacts the profile line. I

When the tracer nger |24 contacts the line |30 the motor will turn thecontrol cam and tracing iingersin a counterclockwise direction becausethe biasing circuit from the positive side of battery |48 through lead|49, switch |50, switch terminal |28 and lead |26 to the tracer linger|24 will be broken. The negative side of the bat- 'switches |68 and |69may be employed to selec-y' A tively operate the motor |20 and therebycontrol l the direction of movement 'of the tracer head relative to thelayout until the tracer lingers |23 and |24 are positioned on oppositesides of the line preparatory to automatic tracing.

The control eiected by rotation of shaft |22 and cam |2| is thatconventionally employed in known types of reproducing machmes whereinthe eccentric form of the cam |2| successively effects shiftingmovements of the valves |56 and |51 for acceleration' of one of themotors 39 or 85 andy corresponding deceleration of the other. Acomplete-360 degree revolution causes successive and `opposite effectsin this respect so that any type o1' contour may be reproduced,continuous rotation of cam causing relative movements of parts toproduce a complete circular outline.

The manner in which the relative pattern controlled movements of tracerand layout determine the hydraulically. effective corresponding relativemovements of work and cutter is diagrammatically indicated in Figure 12.As has been previously described, the movements of the pattern tracermechanism are at right angles-to the corresponding relative movements ofthe work and cutter. In other words, the transverse or forward and backmovement of the layout table determines the longitudinal translation ofthe work support 22 and the longitudinal movement of the tracer headcontrols the transverse movement of the cutter carrying ram.

To effect this result, the sine bar 52 is shown in Figure l2 as disposedat an angle of about 14 degrees to the rectilinear transverse path ofthe layout table 25. A rearward movement of the member 25 under tracercontrol as by actuation of the hydraulic cylinder and piston mechanism36-39 will carry with it the sine bar element 52. As will be evident byreference to Figure 12, this rearward movement will react on shoe 54,moving the shoe to the right and carrying with it the valve plunger 59.The actuating pressure from the pump |65 is supplied through conduit 200to port 20| and branch conduit 202 to port 203 of the servo-distributorvalve mechanism 53.

In the position shown, the valve element 59 is in centralized ornon-feeding position, and it will be noted that the valve shoulders 204and 205 block off any incoming flow of thepressure fluid. The conduits206 and 201 from cylinder 62 are coupled to servo-valve casing 6|.Return of pressure fluid through exhaust port 208 is blocked by thevalvespool 209.

When the layout table 25 moves rearward, the valve 59 will be moved tothe right and the port v 203 will ybe coupled to conduit 206 and the uidwill move piston 03 and work table 22 in a right hand direction. Thiswill likewise move the arm 61 carrying the servo-valve casing 6| to theright,

compensating for the amount of movement im- `parted to shoe 54 by thesliding action of the sine bar and thereby stopping any further movementof the table. It will thus be seen that any continuous or intermittentmovement imparted to the layout, table will eiect a proportionalmovement of the work support with respect to the cutter.

As previously mentioned, if the sine bar 52 isl set at a 45 degreeangle, the movements will be equal in amount, whereas with substantiallya 14 degree angular relationship as indicated in Figure l2, the amountof movement of the work support will be substantially one-fourth that.of the pattern. Any desired ratio or proportion between the movements ofthe respective parts can be controlled by thev angular setting of themem-ber 52. The angular setting of the dial can be determined byreference to a natural trigonometric function table wherein theco-tangent of the Avsine bar angle is the scale of reduction oramplication, whichever the case may be. By this system, any conceivablescale of magnification or reduction from actual size up to inilnity canbedetermined mathematically and quickly set on the sine bars by use ofthe dials.

Correspondingly, the longitudinal movement o the tracer'34 determinesthe nature and extent of transverse or back and forth movement imparted-to the tool carrying ram 28. As has been pointed out, this ktransversemovement of the tracer is eil'ected by the hydraulic motor 65`66 undercontrol of the valve mechanism |56.

.As the tracer head 34 is reciprocated, it carries with it the arm 1|,lthe stud-14 and sine bar segment 15 which. is connected to the sine bar1l. The shoe 80 associated with sine bar 19 is connected tothelservo-valve plunger |56 which cooprates with the casing 0| for thecontrol of the transverse movement of the ram. .Conduits |66 and |60connect opposite ports of the hydraulic4 cylinder`89 to the servo-valvecasing 6|.v The pressure conduit 200 has a rst inlet portion |6|communicating with the lower pressure port of the valve casing 8| and abranch conduit |62 communicating with the upper pressure port thereof.Conduit 2| 0 provides connection from the exhaust port |63 to thereservoir |64.

When the sine bar 19 is moved to the right or left it will cause forwardor rearward movement of the shoe 80 and its associated valve plunger |58which alternately connect either pressure or exhaust ports to therespective cylinder conduits |59 or |60. Since the casing 8| movestransversely with the ram 28, any displacement of the plunger |58 willthereby be neutralized bya corresponding movement of the ram and casing6|. It should be understood that the valve casing 8| is mounted totheram by suitable swivel bracket corresponding in construction to `thatshown in Figure 5 in connection with the servovalve 53 so that each mayautomatically swivel during angular adjustment of its respective sinelbar to maintain a position at right angles or perpendicular thereto. l

In some tracing conditions'the interruption of relative movement betweentracer and layout is magnetic safety valve 2|2 connects with the exhaustconduits 2|3 and 2|4 of the direction and rate valves |56 and |51respectively. In the neutral position shown in Figure l2 the flow oflexhaust uid through the conduit 2| 5 is unrestricted, but as soon asthe motor |20 is energized 'the coil 2|6 may likewise be energized byshifting the switch blade 2 1 to the dotted position shown in Figure 13.This Will connect the coil 2|6 in -series with the motor and clutchwindings through the lead 2|8. Whenever orientation of the tracerfingers |23 and |24 is desirable the motor will -be energized andlikewise the coil 2|6 will magnetically move the `plunger 2|9 of thesafety valve 2|2 downward to block the passage of fiuidvthrough thevalve.

If the movement of the plungers 59 and |66 by their respective sine barsis not rapidly com pensated for by corresponding movement of the valvecasings 6| and 8|, then a further blocking action of the rate andcontrol valves |56 and |61 is desirable. This is accomplished by closingport the tracer head 34 until the work table 22 and l the ram 28 havemoved within the permissible ating sine bars. l

On the switch panel 223 are mounted the switches for control of thehydraulic pump motor and the separate spindle motors. Pilot lights arealso provided to lindicate the operation of the respective motors. A

The amount of eceentricity of the control cam 2| relative to the shaft22 is accomplished by a mechanism conventionally used for tracers ofthis type. It includes a pair of splined axially misaligned sleeves thatare externally positioned by the operation of adjusting segment 222. Thecam may be moved radially from a position of maximum eceentricitywherein the highest rate of feed will be provided to one ofconcentricity with shaft |22 which completely centralizes the rate andcontrol valves |56 and |51 to stop all relative movement between thetracer and layout.

The cutter spindle mounting here illustrated is substantially that shownin my copending applil cation, Serial No. 120,206, which includes theouter rotaryv quills |10 vertically adjustable as by the hand wheels 30having supported therein for eccentric adjustment with respect to thequill, the cutter holding spindles 23 rotated by suitable motor drive tothe pulleys |12 as shown in Figures 1, 2 and 12. lThe quill issurrounded by a worm gear |13 driven by worm |14 on shaft |15 foreffecting rotary adjustment of the quill. This shaft carries bevel gear'|16 meshing withbevel gear |11 on the horizontal splined shaft |18which is journaled in bearings Von the ram`2ii.A This shaft is driven bybevel gear |19 which has an axially slidable splined connection thereto.kThe bevel gear |19 vis mounted for rotation in a housing |80 that isconnected to the horizontal frame From the foregoing it will be apparentthat the present invention provides a completely automatic mechanism forpower following of a contour line or other form of pattern to produceparts that arev either identical in shape and size or complementary toeach other. y

It will be noted that in conjunction with this automatically controlledmechanism` therev has been provided means for producing relativemovement between work support and tool support in two angularly relateddirections, said elements being structurally separated and distinct intheir vmovements from the movements of the pattern and tracer supports.

The invention further provides interconnecting control elements betweenthe respective supports so that movement of the pattern support or thetracer support will transmit to the power control means for theassociated work and cutter supports related directional movements. Thenature of such interconnection, however, is such that the extent, amountor ratio of movement of a controlled support with respect to acontrolling support may be readily and independently varied or adjustedas desired so that the movements may be either actual size, magnified orreduced 32. `'I'he housing also provides'suitable bearing for thevertical shaft |8|, the upper end of which carries the bevel gear |82that meshes with bevel gear |19. A spiral gear |83 is connected to thelower end of shaft |8| and meshes with the mating spiral gear |84 thatis firmly connected to the splined shaft |85. 'I'he spur gear |86 issplined to the shaft |85 so as to have free axial movement thereon andis meshed with the spur gear |81 that is connected to the shaft |88rthat carries the worm |36. The shaft |85 has its bearing at one end inthe casing |80 and at the opposite end in a bracket likewise mounted tothe horizontal framev32.l In each step of the gear transmission a one toone ratio is maintained so that the shaft |22 and the connected tracervfingers |23 and |24 move in perfect angular synchronism with the quillsi1 I. It is also imperative that the plane of eceentricity adjustment ofthe cutter spindle 29 in the quills |1| is parallel to the direction oftracing indicated by. the 'arrow on control cam |2 v It will thus benoted that the tracer unit 34 y and the ram 28 may have independentlongitaneously produced in exact accordance as to shape and'size forproper interiltting or cooperative utilization. v

to produce desired variations in the size of the work piece producedwith respect to size of the controlling pattern. Additionally, byaccurate independent adjustment of the respective controls, the shape ofthe produced Work piece may be made to correspond exactly with the shapeof the pattern, or by a different ratio of movements of one of thecontrolling and controlled slides, variations in contour or shape of thefinished work piece may 'be produced from a single a pattern.

It will also be evident that the work piece or work pieces may besuitably mounted on their support and the pattern on its support inapproximate desired relationship one to the other and the positioning ofthe respective controlling and controlled supports subsequently adjustedto bring the relationship of tool to work piece in exact desiredrelation to the position of the controlling tracer mechanism withrespect to the pattern.

It will be further noted thatv the particular relations'hip shown inwhich a controlling slide has its movement in a direction at rightangles to a controlled slide makes possible the utilization of arelatively simple translatable sine bar and valve shoe mechanism fordirect transmission of the desired proportionate movement of relatedelements.

The self compensating valve connection between the controlling andcontrolled supports permits the use of a sensitive tracing mechanism foraccurately following the pattern and the utilization of'a powerfuldriving action for machining the work piece without the introduction oferror or lost motion'between the related supports.

This' combination is particularly advantageous when the dimensions ofthe Work piece are greater than that of the controlling pattern.

The verner graduated dial for adjustment of the angular position of thesine bar permits the operator to set the scale of translation at any oneof an infinite combination of scales for either amplification orreduction. As pointed out bea fore, the angular value of the sine barand the dial setting is readily determined from the cotangent of thedesired scale.

What is claimed is:

1. A reproducing machine, including a bed,l a

tions, power` means independent of the iirst power means for effectingsaid relative movements and adjustable power controls intervening thepattern and tracer supports and said independent power means fordetermining the proportional actuation of the work and tool supports bysaid independent power means.

2. A reproducing machine, including a bed, a pattern support and atracer support, means mounting said supports on the bed for relativemovement, power means for eiecting relative movement of the supports, atracer carried by the tracer support in position to cooperate with a4pattern on the pattern support, connections between the tracer and saidpower means for automatic determination of relative movement of thesupports, a work support and a tool support, means mounting saidsupports on the bed for relative-movement in angularl; relateddirections, power means independent of the first power means foreffecting said relative movements, and adjustable power controlsintervening the pattern and tracer supports and said independent powermeans for determining the proportional actuation of the work and toolsupports by said independent power` means,l said power controlsincluding adjustable sine bar elements individual to said powercontrols.

3. A reproducing machineincluding a bed, a work support translatablymounted thereon, a pattern support mounted on the bed for movement in adirection at right angles to the direction of movement of the worksupport, means for effecting movement 'of the pattern support,-

independent power means for effecting movement of the work support, anadjustable sine bar controlmeans carried by and movable with the patternsupport, a power control means carried by and movable with the worksupport having a portion disposed in cooperative relation with said sinebar,` and operative connections betweensaid control means and the poweractuating means for the work support whereby on movement of the patternsupport sine bar actuation of the control means will determine the rateand extent of movement of the work support. Y

4. A reproducing machine including a bed, a work support translatablymounted theron, a

pattern support mounted on the bed for movecarried by and movable withthe work support having agportion disposed in cooperative relation `withsaid sine bar, operative'connections between said control means and thepower actu-4 'ating means for the work support whereby on movement ofthe pattern support sine bar actuation ofthe control means .willdetermine the lrate and extent of movement of the work support, andmeans forvarying the angular relationship between the sine bar andpattern supment in a direction at right angles to the direction ofmovement of the work support, means for eiiecting movement of thepattern support,

independent power means for effecting movement of the work support.anadjustable sine bar lcontrol means carriedby and movable with thepattern support, a power control means carried by and movablev with thework support having a portion disposed in cooperative relation with saidsine bar, operative connections between said control means and the poweractuating means for the work support whereby on movement of the patternsupport sine bar actuation of the control means will determine the rateand extent of movement of the work support, means for varying. theangular relationship between the sine bar andpattern support to vary theproportional rates of movement of the respective supports, and meanspivotally mounting the sine bar actuated control means whereby the samemay remain substantially normal to the sine bar for different angularlyadjusted positions of the sine bar.

6. A reproducing machine including a bed, a first pair of supportsincluding a tracer support and a pattern support, means mounting said`supports on the bed for relative movement in two angularly relateddirections, a second pair of supports including a tool support and awork support, means mounting said secondv pair of supports on the bedfor relative movement in two angularly related directions, tracercontrolled means for determining relative movements of the first pair ofsupports, independent power means `for determining relative move-- mentsof each of the second pair of supports, an independent control devicefor each of said independent power means, each of said control devicesincluding a servo follow-up mechanism, a rst actuating mechanismcoupling one of said first-mentioned pair of supports with the followupmechanism for one of the latter mentioned pair of supports, a secondactuating mechanism coupling the other of said rst-mentioned pair ofsupports with the follow-up control for the other of said second pair ofrelatively movable supports for actuation thereof, and means foradjusting the control mechanisms for the second pair of supports to varythe relative rates of movement of the tlrst and second pairs ofsupports.

7. A reproducing machine including a bed, a first pair of supportsincluding a tracer support and a pattern support, means mounting saidsupports on the bed for relative movement in two angularly relateddirections, a second pair of supports including a tool support and awork support, means mounting said second pair ci supports on the bed forrelative movement in two angularly related directions, tracer controlledmeans for vdetermining relative movements of the first pair of supports,independent power means for determining relative movements of each ofthe second pair of supports, an independent control device for each ofsaid independent power means, each of said control de- Vices includingIa servo follow-up mechanism, a

first actuating mechanism coupling one of said first-mentioned pair ofsupports withlthe followup mechanism for one of the latter mentionedpair of supports, a second actuating mechanism coupling the other ofsaid first-mentioned pair o! supports with the follow-up control for theother oi' said second pair of relatively movable supports for actuationthereof, a first means for varying the effective reaction of the controlmeans on the follow-up device as respects a support of the first pairand the coupled support of the second pair and a second means forindependently varying the reaction of the follow-up device interveningthe other supports of the first and the second pairs whereby therelative rates of movement of the respective supports of the first pairand second pair may be independently varied.

8. A machine of the character described in- .cluding a bed, a firstsupport mounted on the bed for translation relative thereto, a secondsupport mounted on the bed for translation relative to the bed in adirection at right angles to the direction of movement of the iirstsupport, means for moving the first support with respect to the bed, anangularly adjustable sine bar carried by said first support and movabletherewith, an actuating means for said second support including an armcarried thereby and extending into proximity with the first support, anda guide carried by said arm and engaging the sine bar to determine theproportional movement of the second support with respect to the movementof the first support.

9. A machine of the character described including a bed, a first supportmounted on the bed for translation relative thereto, a second supportmounted on the bed for translation relative to the bed in a direction atright angles to the direction of movement of the first support, meansfor moving the rst support with respect to the bed, an angularlyadjustablesine bar carried by said first support and movable therewith,an actuating means for said second support including an arm carriedthereby and extending into' proximity with the first support, a guidecarried by said arm and engaging the sine bar to determine theproportional movement of the second support with respect to the movementof the first support, power means for effecting movement of said secondsupport, and a controller for said power means including a firstshiftable element associated with and movable by the guide forinitiating power movement of the second support, and a follow-up membercarried by the arm and shiftable with the support for interrupting theaction of the power means.

l0. A reproducing machine of the character described including a bed acontrol support and a controlled support movably mounted on the bed, afirst means for determining movement of the control support, independentmeans for effecting` movement of the controlled support, and means fordetermining the proportional movements of the supports,` including arotary sine bar support, means mounting said sine bar support formovement with and rotation with respect to the control support, a sinebar carried by the sine bar support, means for effecting micrometerangular adjustments of the sine bar, power means for effectingl movementof the controlled support, and a rate and direction determinator forsaid power means including a follow-upl member carried by and movablewith the control support, and an actuator translatably supported'therebyhavtion with respect to the bed, a layout table supported by the bed fortranslation in a direction at right angles to the direction of themovement of the work support, a tool carrying ram mounted on the bed fortranslation in a direction at right angles to the direction of movementof the work support whereby any desired .relative angular movements maybe effected between tool support and work support, a tracer supportmounted on the bed in overlying relation to the layout support, meansmounting the tracer support 4for translation in an angularly relateddirection as respects the direction; of translation of the layoutsupport with respect to the bed, a guide member pivoted to the layoutsupport and movable therewith, means for angularly adjusting the guidemember with respect to the layout member, a control arm mounted on thework support and extending in the direction of the layout support, saidcontrol arm having a guide shoe interengaged with the angularlyadjustable guide member for control of movement of the work support, andmeans for adjusting said arm with respect to the work support to varythe effective relationship between the pattern support and the worksupport.

12. A reproducing machine including a bed, a work support mounted forlongitudinal translation with respect to the bed, a layout tablesupported by the bed for translation in a direction at right angles tothe direction of the movement ofthe work support, a tool carrying rammounted on the bed for translation in a direction at right angles to thedirection-of movement of the work support whereby any desired relativeangular movements may be eifected between tool support and work support,a tracer support'mounted on the bed in overlying relation to the layoutsup'- port, means mounting the tracer support for translation in anangularly related direction as respects the direction of translation ofthe layout support with respect to the bed, a guide member pivoted tothe layout support and movable therewith, means for angularly adjustingthe guide member with respect to the layout member, a control armmounted on the work support and extending in the direction of the layoutsupport, said control arm having a guide shoe interengaged with theangularly adjustable guide member for control' of movement of the worksupport, means for adjusting said arm with respect to the Work supportto vary the effective vthe ram, and a ram rate controller carried by theram, having a follower engaging the guide bar and actuable thereby tocontrol the operation of said power operating means.

13. A reproducing machine including a control slide and a controlledslide, tracer controlled means for determining the direction and extentof movement of the control slide, an independent power actuator for thecontrolled slide, a rate 15 and direction determinator for the movementoi the controlled slide. and means carried by the control slide foroperating said determinator.

14. A reproducing machine including a control slide and a controlledslide, .tracer controlled means for determining the direction and extentof movement of the control slide. an independent power actuator for thecontrolled slide, a rate and direction determinator for the movement ofthe controlled slide, means carried by the control slide for operatingsaid determinator. and means for varying the ratio of operation of thedeterminator eiected by the control slide as respects the movementimparted to the control slide.-

l5. A reproducing machine including a first each of said controlledslides, a control device connecting one of the control slides with thedeterminator of one of the controlled "slides, a control deviceconnecting the other of the control slides with the determinator of theother oi! the controlled slides. and means for independently varying thereaction of said control-devices as respects the individualdeterminators of power actuation means of the respective controlledslides.

16. A reproducing machine including a rst pair of control slides movablein angularly re- 1B lated paths, tracer controlled powermeans fordetermining the relative movements of the slides and thus the resultantpath oi.' movement thereof, a pair of controlled slides, independentpower means for actuation of said slides, movement ,determinatorsindividual to the power means for each of said controlled slides, acontrol device connecting 'one of the control slides with thedeterminator of one of the controlled slides, a control deviceconnecting the other of the control slides with the determinator of theother of the controlled slides, and means for independently varying thereaction of said control devices as respects the individualdeterminators of power actuation means of the respective controlledslides, each of said determinators including a feed back device carriedby its controlled slide for limiting the movement of the controlledslide initiated through its respective control device by movement of itsconnected control slide.

DALLAS R. TRINKIE.

REFERENCES CITED The following references are of record in the le ofthis patent:

UNITED STATES PATENTS Eberlein Oct. 25, 1949

